CN101680361A - damped planetary transmission - Google Patents

damped planetary transmission Download PDF

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Publication number
CN101680361A
CN101680361A CN200880018733A CN200880018733A CN101680361A CN 101680361 A CN101680361 A CN 101680361A CN 200880018733 A CN200880018733 A CN 200880018733A CN 200880018733 A CN200880018733 A CN 200880018733A CN 101680361 A CN101680361 A CN 101680361A
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CN
China
Prior art keywords
planetary transmission
input element
damped
vibration isolator
input
Prior art date
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Granted
Application number
CN200880018733A
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Chinese (zh)
Other versions
CN101680361B (en
Inventor
A·塞科
P·A·沃德
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Gates Corp
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Gates Corp
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Publication date
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Publication of CN101680361A publication Critical patent/CN101680361A/en
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Publication of CN101680361B publication Critical patent/CN101680361B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

Disclosed is a damped planetary transmission comprising an input member, an inertial member connected to the input member, a planetary gear assembly connected to the input member, the planetary gear assembly comprising a carrier member that is directly and fixedly connected to the input member, a brake member engaged with a ring gear of the planetary gear assembly, the planetary gear assembly connected to an output member, a one-way clutch operationally disposed between the input member and the output member, and a vibration isolator directly connected for torque flow between the input memberand the one-way clutch.

Description

Damped planetary transmission
Technical field
The present invention relates to a kind of damped planetary transmission, and relate more specifically to have the planetary transmission of vibration isolator, this vibration isolator directly is connected for the torque-flow between input element and the overrunning clutch.
Background technique
Changeable planetary transmission is intended to give when the race of engine annex to provide sufficient power such as air condition compressor and alternator, thereby does not cause that these annexes are with high engine speed operation causing damage simultaneously.This feasible operation that can guarantee vehicle electrical system is even also be like this when the annex size reduces.
It drives provides the changeable planetary transmission of damping from US 6 for the torsional vibration that takes place from crankshaft, 250, known in 276 (2001), it discloses a kind of driving mechanism that is used for the annex of reciprocating internal combustion engine, it has changeable planetary transmission, and this gearbox and crankshaft are located with one heart and driven by the latter.In order to prevent that the vibration that free-ended noise of crankshaft and wearing and tearing produce from arriving planetary transmission, be arranged between crankshaft and the planetary transmission as the vibration isolator of cross recess colligator.Yet US 6,250, and the gearbox in 276 provides a kind of vibration isolator that is arranged between crankshaft and the planetary pinion carrier, and this has increased the complexity and the size of gearbox, and this has just increased manufacture cost.
Need a kind of planetary transmission with vibration isolator, this vibration isolator is connected directly the torque-flow that is used between input element and the overrunning clutch.The present invention has satisfied this demand.
Summary of the invention
Main aspect of the present invention provides a kind of vibration isolator that is used for the torque-flow between input element and the overrunning clutch that is connected directly.
Others of the present invention will be pointed out or become obvious by description below the present invention and accompanying drawing.
The present invention includes a kind of damped planetary transmission, it comprises: input element; Be connected to the inertance element of input element; Be connected to the planetary gear set of input element, described planetary gear set comprises directly and is fixedly connected to the carrier element of input element; The braking member that combines with the ring gear of planetary gear set; Be connected to the planetary gear set of output element; Operationally be arranged in the overrunning clutch between input element and the output element; And the vibration isolator that directly is connected for the torque-flow between input element and the overrunning clutch.
Description of drawings
Be incorporated into specification and constitute its a part of accompanying drawing and show the preferred embodiments of the present invention, and be used for explaining principle of the present invention with describing.
Fig. 1 is the perspective cross-sectional view of gearbox.
Fig. 2 is the decomposition view of gearbox.
Fig. 3 is the cross section of gearbox.
Fig. 4 is the perspective view of gearbox and band brake.
Fig. 5 is the schematic representation that is used for the control system of gearbox.
Fig. 6 is the cross section of gearbox.
Embodiment
Fig. 1 is the cross section of gearbox.Gearbox 100 is the compact unit that are installed on the end of combustion engine crank axle.
Gearbox 100 comprises input element 13.Input element 13 uses bolt 11 to be connected to engine crankshaft.Inertance element 12 is connected to input element 13.
Input element 13 also comprises carrier element 13a.Input element 13, inertance element 12 and carrier element 13a connect to form input assembly.Carrier element 13a is the part of input element 13.
A plurality of planetary pinions 14 are arranged in around the carrier element 13a.Each planetary pinion 14 is around main shaft 15 rotations.
Ring gear 16 radially is arranged in the outside of carrier element 13a.Each planetary pinion 14 combines with ring gear 16 and sun gear 17.
Ring gear 16 is rotating around carrier element 13a on bearing 20 on the bearing 18 and for output element 19.
Carrier element 13a, planetary pinion 14, main shaft 15 and ring gear 16 comprise planetary gear set.
Band brake 24 combines with the outer surface 25 of ring gear 16.
Sun gear 17 is arranged on the output element 19.
Output element 19 comprises belt bearing surface 21.The belt bearing surface can have any required profile, comprises as directed many ribs profile.
Overrunning clutch 22 directly is arranged between vibration isolator 23 and the output element 19.Vibration isolator 23 directly is arranged between overrunning clutch 22 and the input element 13.This layout makes vibration isolator 23 damped vibrations, otherwise this vibration will be impacted overrunning clutch 22, thereby prolongs the life time of overrunning clutch 22.This is not arranged and can as instruction in the prior art carrier 13a be separated with crankshaft (CRK).
This creationary gearbox has two operator schemes.The firstth, band brake not in conjunction with the time.The secondth, band brake in conjunction with the time.
First operator scheme
In first operator scheme, crankshaft (not shown) rotation input element 13, and so rotating carrier element 13a.Inertance element 12 is subordinated to input element 13 and will can describe in addition.
Because band brake does not have combination, ring gear 16 freely rotates.
In this pattern, overrunning clutch 22 is combined, causes that therefore output element 19 as one man and with identical with it speed rotates with input element 13.
Because described gearbox is connected to the crankshaft of internal-combustion engine by bolt 11 and unshowned displacement pin, gearbox 100 is exposed to by the caused intermittent torsional vibration of lighting a fire of the intermittence of each cylinder.Torsional vibration is harmful to for the parts in the gearbox (being overrunning clutch 22).Intermittent torsional vibration causes the oscillatory rapid change in the rotational speed of input element 13.
Vibration isolator 23 comprises elastic element 23a, and it is compressed between outer member 23b and the inner member 23c.Vibration isolator 23 and especially elastic element 23a are around input element 13.Elastic element 23a absorbs crankshaft torsional vibrations, transfers to overrunning clutch 22 and output element 19 thereby reduce or eliminate torsional vibration.
Vibration isolator 23 damps torsional vibrations, otherwise the torsional vibration meeting is transmitted but can not pass through carrier element 13a, because inner member 23b is the integral part of input element 13 by overrunning clutch 22 transmission.In other words, vibration isolator 23 not dampings transfer to the vibration of carrier element 13a from input element 13.Vibration isolator 23 is damps torsional vibrations during first operator scheme mainly, but then can not during second operator scheme.Vibration isolator 23 operationally transfers to output element 19 with moment of torsion from input element 13 when overrunning clutch 22 is combined.
In first operator scheme, torque-flow directly passes through vibration isolator 23, passes through output element 19 then to the belt (not shown) by overrunning clutch 22 from input element 13.
Second operator scheme
In second operator scheme, band brake 24 is combined.This prevents ring gear 16 rotations.When ring gear 16 lockings, the rotation of carrier element 13a causes that each planetary pinion 14 is around each corresponding main shaft 15 rotation.The rotation of each planetary pinion 14 causes that sun gear 17 is driven on the sense of rotation identical with input element 13, but the bigger speed of 2:1 ratio is driven to have roughly.Because sun gear 17 and output element 19 are to be activated than input element 13 bigger speed, so overrunning clutch 22 overloads and separation.
The such as described damps torsional vibrations of vibration isolator 23.
In second operator scheme, torque-flow passes through planetary pinion 14, passes through sun gear 17 to output carrier 19 from input element 13 (thereby and by carrier element 13a).Because overrunning clutch 22 separates, and does not have torque transfer to pass through overrunning clutch 22.Therefore, vibration isolator 23 can damps torsional vibrations in second operator scheme.The crankshaft vibrations of reversing is carried out damping by inertance element 12 in second operator scheme.
Fig. 2 is the decomposition view of gearbox.Snap ring B and G are known in the prior art.Sealing F and H prevent that fragment from entering gearbox.Sleeve D and E are as Sealing between the rotary component and bearing surface.Axle collar A is used for bolt 11 is positioned in the input element 13.Bolt 11 is arranged coaxially with the spin axis of gearbox.Sealing C prevents that fragment from entering gearbox.
Fig. 3 is the cross section of gearbox.Output element 19 rotates on bearing 26.Bearing 26 is arranged between input element 13 and the output element 19.
The torsional vibration of inertance element 12 damping crankshaft CRK.Inertance element 12 is known in the prior art and generally include a block 12a, and this block 12a is connected to plate 12c by complying with element 12b.Comply with element 12b and generally include elastic polymer material, such as natural rubber or synthetic rubber or their combination.
In this Fig. 3, it is the alternate embodiment of the inertance element 12 shown in Fig. 1 that inertance element 12 is depicted as.Unique difference between two embodiments is, for the spin axis of gearbox, among Fig. 1 element roughly axially extend and in Fig. 3 element roughly radially extend.Each embodiment equally well moves and can select any according to the serviceability of the motor that it was mounted thereon.
Band brake band 24 combines with the surface 25 of ring gear 16.The band brake band can comprise known one of prior art.For example, full content is by with reference to being incorporated into disclosed band brake in this U.S. Patent No. 4,881,453.
Part 27,28 and 30 prevents that fragment from entering gearbox, and support structure is provided.
Fig. 4 is the perspective view of gearbox and band brake.Combining with the surface 25 of ring gear 16 of band brake 200 with 24.Band comprises friction material 24a.
Band brake 200 is by vacuum actuator 201 operations.Vacuum actuator 201 is connected to by connecting rod 202 and is with 24.Connecting rod 202 is by director element 203 guiding.Director element 203 limiting rods 202 are so that connecting rod 202 moves on the substantial linear direction along its main axis A-A.Be with 24 to be connected to pedestal 206 at first pivot, 204 places.With 24 second pivots 205 that are connected on the end of connecting rod 202.
The linearity of connecting rod 202 moves and causes closely combination surface 25 of second pivot 205.Under the situation that does not have director element 203, second pivot 205 can radially outwards be promoted by surface 25 during operation, and this can reduce the usefulness of belt actuator again.
The pedestal 206 of band brake 200 uses bolt 207 to be mounted to installation surface, such as motor.
Vacuum actuator 201 is connected to vehicle vacuum system and controls according to engine speed.
Fig. 5 is the schematic representation that is used for the control system of gearbox.Vacuum actuator 201 is connected to vehicle vacuum system 210.Vacuum actuator also is connected to E3 controller 300 well known in the prior art.E3 controller 300 is connected to Vehicular battery 301.
Velocity transducer 302 provides engine speed signal for the E3 controller.The E3 controller can be programmed, to activate vacuum actuator 201 according to predetermined engine speed.For instance, when the race of engine, belt actuator " unlatching " and therefore vacuum actuator " unlatchings " and be with 24 to combine with surperficial 25.This has stopped the rotation of ring gear 16.This causes that output element 19 is with the speed rotation bigger than the speed of input element 13.This causes that annex is activated with the speed that is fit to when the race of engine.The race of engine normally～700RPM to 900RPM.Transmission ratio is usually in about 2: 1 scope.
During greater than～2000RPM, vacuum actuator " is closed " in speed, and this allows ring gear 16 rotations.Engine speed signal is from velocity transducer 302.The rotation of ring gear 16 causes that output element 19 is with the speed rotation identical with input element 13.Yet because the more minor radius of output element 19, annex is activated with slower speed usually, thereby reduces with the required amount of power usually of high engine speed operation annex more.The diameter of output element 19 normally～90 millimeter.By contrast, the representative diameter of crankshaft pulley is in 150 millimeters to 175 millimeters scope roughly.
Fig. 6 is the cross section of gearbox.In this alternate embodiment, vibration isolator 230 comprises the torsion spring that replaces elastic material.Torsion spring at one end 232 places is connected to input element 13 and is connected to sleeve 231 at the other end 233 places.Sleeve 231 and overrunning clutch 22 are non-to be combined slidably.Vibration isolator 230 comes damps torsional vibrations by the vibration of twining and decontrol spring.The damping speed of vibration isolator 230 is its torsion spring function of speed.
Though described form of the present invention here, to those skilled in the art obviously, do not broken away under the present invention such as the spirit and scope described herein and can make variation to the structure of parts and relation and method.

Claims (9)

1. damped planetary transmission, it comprises:
Input element;
Be connected to the inertance element of input element;
Be connected to the planetary gear set of input element, described planetary gear set comprises directly and is fixedly connected to the carrier element of input element;
The braking member that combines with the ring gear of planetary gear set;
Be connected to the planetary gear set of output element;
Operationally be arranged in the overrunning clutch between input element and the output element; And
Directly be connected for the vibration isolator of the torque-flow between input element and the overrunning clutch.
2. as the damped planetary transmission in the claim 1, wherein, vibration isolator can be operated, so that when overrunning clutch is combined moment of torsion is transferred to output element from input element.
3. as the damped planetary transmission in the claim 1, wherein, planetary gear set comprises the sun gear that is fixedly connected to output element.
4. as the damped planetary transmission in the claim 1, wherein, braking member comprises:
Vacuum actuator with the connecting rod that is connected to band edge;
Director element, it combines with connecting rod, thus the mobile of band edge is substantial linear; And
Use engine speed by controller control brake element.
5. as the damped planetary transmission in the claim 1, wherein, vibration isolator comprises torsion spring.
6. as the damped planetary transmission in the claim 1, wherein, vibration isolator comprises elastic element.
7. as the damped planetary transmission in the claim 1, wherein, output element comprises pulley.
8. as the damped planetary transmission in the claim 1, wherein, input element is connected to engine crankshaft.
9. as the damping planetary transmission in the claim 1, wherein, inertance element comprises elastic part.
CN2008800187330A 2007-06-04 2008-05-14 Damped planetary transmission Active CN101680361B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US93310307P 2007-06-04 2007-06-04
US60/933,103 2007-06-04
PCT/US2008/006131 WO2008150349A1 (en) 2007-06-04 2008-05-14 Damped planetary transmission

Publications (2)

Publication Number Publication Date
CN101680361A true CN101680361A (en) 2010-03-24
CN101680361B CN101680361B (en) 2012-07-18

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CN2008800187330A Active CN101680361B (en) 2007-06-04 2008-05-14 Damped planetary transmission

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US (1) US7758465B2 (en)
EP (1) EP2162605B1 (en)
CN (1) CN101680361B (en)
AT (1) ATE498767T1 (en)
DE (1) DE602008005018D1 (en)
WO (1) WO2008150349A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103328859A (en) * 2011-01-20 2013-09-25 舍弗勒技术股份两合公司 Method for controlling a planetary gear in a belt drive and belt drive
CN105134921A (en) * 2015-09-30 2015-12-09 哈尔滨广瀚动力传动有限公司 Planet carrier vibration-isolation mounting structure
CN107664197A (en) * 2016-07-27 2018-02-06 通用汽车环球科技运作有限责任公司 transmission assembly with damping material

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US8313400B2 (en) * 2008-11-13 2012-11-20 The Gates Corporation Damped isolator
GB2469872A (en) * 2009-05-01 2010-11-03 Antonov Plc A transmission unit for relaying drive from a cranksgaft of an internal combustion engine to engine ancillaries
DE102009042682A1 (en) * 2009-09-23 2011-03-24 Man Nutzfahrzeuge Ag Drive device for at least one secondary drive
US9631563B2 (en) 2010-06-30 2017-04-25 Orbital Traction, Ltd Torque pulse dampener
US8403800B2 (en) * 2010-07-28 2013-03-26 The Gates Corporation Shift mechanism for a planetary gear transmission
US9284994B2 (en) 2011-04-04 2016-03-15 Litens Automotive Partnership Clutch mechanism and decoupler device with same
KR101490948B1 (en) * 2013-09-09 2015-02-12 현대자동차 주식회사 Damper pully assembly of vehicle
WO2015070329A1 (en) 2013-11-14 2015-05-21 Litens Automotive Partnership Decoupler with overrunning and belt-start capability with simplified construction
US10378620B2 (en) 2014-01-10 2019-08-13 Litens Automotive Partnership Decoupler with overrunning and belt-start capability
US9688394B2 (en) 2015-07-16 2017-06-27 Honeywell International Inc. Roller-based drive systems with compliance for accommodating non-conjugate meshing
KR101755884B1 (en) * 2015-11-13 2017-07-07 현대자동차주식회사 Damper Pulley Assembly For Vehicle
IT201700021137A1 (en) * 2017-02-24 2018-08-24 Dayco Europe Srl FILTERING PULLEY
US10830126B2 (en) * 2018-06-29 2020-11-10 Schaeffler Technologies AG & Co. KG Two-speed accessory drive pulley
DE102022212522A1 (en) * 2022-11-23 2024-05-23 Zf Friedrichshafen Ag Gear or shaft with vibration damper

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103328859A (en) * 2011-01-20 2013-09-25 舍弗勒技术股份两合公司 Method for controlling a planetary gear in a belt drive and belt drive
CN103328859B (en) * 2011-01-20 2016-08-24 舍弗勒技术股份两合公司 Method for controlling a planetary gear in a belt drive and belt drive
CN105134921A (en) * 2015-09-30 2015-12-09 哈尔滨广瀚动力传动有限公司 Planet carrier vibration-isolation mounting structure
CN107664197A (en) * 2016-07-27 2018-02-06 通用汽车环球科技运作有限责任公司 transmission assembly with damping material

Also Published As

Publication number Publication date
WO2008150349A1 (en) 2008-12-11
DE602008005018D1 (en) 2011-03-31
US7758465B2 (en) 2010-07-20
CN101680361B (en) 2012-07-18
US20080300098A1 (en) 2008-12-04
EP2162605B1 (en) 2011-02-16
ATE498767T1 (en) 2011-03-15
EP2162605A1 (en) 2010-03-17

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